Rotary pump or compressor



Dec. 10, 1935. J. F. JAWO ROWSKI ROTARY PUMP OR COMPRESSOR Filed March 5, 1954 2 Sheets-Sheet 1 m mm 31 J. F/JAWOROWSKI ROTARY PUMP OR COMPRESSOR Filed March 5, 1934 2 Sheets-Sheet 2 v Patented Dec. 1935 PATENT OFFICE,

ROTARY PUMP on COMPRESSOR Joseph F. Jaworowski, Cleveland, Ohio, assignor of twenty-five per cent to Samuel E. Dettelbach and twenty-five per cent to Sam Emerson, both of Cleveland, Ohio Application March 1934, Serial No. 714,132 4 Claims. (c1. 103-144) My invention relates to an improvement in rotary pumps or compressors, and more particularly to that type of pump or compressor, comprising a circular working chamber in which'a rotary piston is adapted to operate to compress or transfer a, liquid or other fluid, as disclosed in my 'co-pending application, Serial No. 644,199, filed November 25, 1932.

The general object of the present invention is to provide a smooth running pump of economical construction, which can be easily assembled and disassembled, and wherein a high degree of pumping efliciency may be maintained and the life and durability. of the working parts prolonged.

Other objects and advantages of the invention will be apparent as the following description is considered in connectionwith the accompanying drawings, in which:

Figure 1 is a side view of the pump with one of the side plates removed to expose the working parts of the pump;

Figure 2 is a longitudinal section taken onthe line 22 of Figure 1;

Figure 3 is a plan view of the three rotatable blades inassembled relation; I

Figures 4', 5, and 6 are end and side views of the respective blades shown in Figure 3, rotated to a position in Figure 5 disclosing the mounting of the hub of the male blade between the hubs of the female blades;

Figure 7 is a front .view of the male blade; and Figure 8 is a front view of one of the female blades.

My improved pump comprises a cast metal body 2, having flat side faces or walls 3 and a circular opening 4, extending centrally through the casting. Fluid is received into the pump through an intake passage 5- and discharged therefrom through a discharge passage 6, each of which communicates with the circular opening or cylinder chamber 4. The passages 5 and 6 are separated from each I, as best seen in Figure 1. 8 and 9 detachably secured to the side faces or walls 3 of cast body 2, by means of bolts l enclose the opposite ends of chamber 4.

Separate cover plates The flow of fluid from the intake to the outletside of the pump is effected by means of piston blades B, preferably three in number, and a cylindrical-hollow rotor II adapted to revolve or be revolved within cylinder chamber 4. Rotor H is of smaller diameter than the chamber 4 and 'it rotates on a fixed axis offset or eccentric to the axis of chamber 4 so that the periphery of the rotor is always in close contact with the inner face other by a transverse wall male'blade is provided with two bosses or shoes 36 symmetrically arranged with respect to the hub portion 33. The inner ends of these blades are hinged together or pivotally connected to a bushing I 6 adapted to rotate about a pin or shaft l1, the axis of which is co-incident with the axis of cylinder 4 so that the piston blades may always. maintain their radial position and rotate freely upon the axis without binding against the wall of cylinder 4. There will always be a clearance between the blade and the wall of cylinder 4,

and this clearance will be particularly marked in pumps of large size. The rotor II is mounted at one end upon a shaft 18, having rotatable bearing in a boss or extension l9, on cover plate 9 and is adapted to be driven by power in any desired way. The inner end of this shaft is fixed to the rotor H by a key 39 held in place by a bolt 40. The moving parts thus revolve about their own center of gravity. Any appropriate number of blades B may be employed. Extension l9 constitutes a stuifing box which will be described later on.

The pin or shaft I! to which the piston blades are hinged is an integral offset extension of a short .shaft 20 which latter shaft is held against rotation tightly within a hub portion 2| on cover plate 8, a pin 22 being used for such purpose. I

This end of the rotor is open and the shaft 20 extends through a bearing 24 in the opening and n over which a tubular cover member 2| for the' rotor is tightly sleeved. 'I'hiscove'r member 2| is secured to said rotor by means ofset screws 25.

A chamber 21 formed in body 2 adjacent inlet passage 5 by a downwardly and inwardly pro- J'ecting longitudinal curved wall 28, serves to check suction oscillations at the intake side of the pump, thus reducing chattering to a mini- I passage 29, thus forming an air or gas cushion-' ing pocket which serves to counter-act suction oscillations at the intake side of the pump caused by the variations in suction of the rotor II and its set of piston blades B. This insures a steady fiow of liquid through inlet passage 5 into cylinder 4.

When the rotor I I revolves, the off center position of the rotor within cylinder 4 causes the piston blades to oscillate in respect to each other and the rotor and a relative sliding movement also occurs between the rotor and the piston blades, the latter being merely oscillated on the fixed pin-or shaft H as they are forced to travel in a circular path or orbit by the rotatable movementof the rotor on its 'own axis which, as previously explained, is offset from the common axis of the cylinder and blades. A predetermined amount of fluid may thereby be pumped or transferred from the intake passage to the discharge passage through the crescent shaped working chamber 12 during each revolution of the rotor. During this movement of the rotor, the radially arranged piston blades B are carried around in a circular path within cylinder 4, constant contact between the rotor and the blades being of course necessary to prevent chattering. To this end the blades are formed with round shoulders or bosses 3| co-extensive in length with and ad- V jacent the outer faces 32 of the piston blades.

These longitudinally extending shoulders rockingly engage the opposing parallel walls of the respective straight radially disposed slots I5 and consequently all wear is evenly distributed. This constitutes a distinct improvement over the structure disclosed in my co-pending application Serial No. 644,199, wherein flat'faced blades and angular or shouldered slots are employed. This latter arrangement proved troublesome because of the wear being concentrated at the angular or shouldered portions of the slots thus necessitating repairs to or replacement of the rotor.

- form thestraight walled type of radial slot. It

'will of course be understood that the construction of the rotor I I and blades B is such that the inner ends of the latter are permitted to assume different angular positions with respect to the rotor.

As previously explained the piston blades -B are adapted to operate within the longitudinal slots I5 the full length of the rotor. That is to say, the working areas of the blades are co-extensive with the cylinder 4 in pump body 2, which places the end edges of the wing portions of the blades in a relatively close seating position against the flat inner walls of the cover plates 8 and 9. The somewhat shortened inner portions of the piston blades provide hinge portions, which in the male piston blade embodies a single centrally disposed hub member 33, whereas the female piston blades 23 each have two spaced inner and outer hub members 34 and 35 respectively. These hub portions are sleeved over the bushing I6 which is sleeved over the stationary shaft or pin I1 extending axially into the cylinder 4. When the parts are assembled the connecting hinge or hub portions for the piston blades are confined within rotor II, but have suflicient clearance to permit the blades to oscillate freely.

It will be noted that the female blades 3 are bearing of this blade. All danger of damage to of identical construction and can therefore be made from the same pattern. Also that each female blade 23 includes two hub portions 34 and 35, so arranged with respect to the length of said blades, that a plane extending at a right 5 angle to the blade and equally spaced from the ends thereof is offset approximately half the width of one of said hubs from a similar or par allel plane equally spaced from the hub portions of the blade. The periphery of the hub 34 of each 19 female blade 23 is machined to provide a smooth bearing surface 26 for the shoes 36 of male piston blade I3. When this surface is accurately finished all danger of the blade touching the cylinder wall will be eliminated. 15

Assembly is effected by first reversing the lengthwise position of one blade 23 with respect to the other blade 23, and then moving these blades to the position best shown in Figures 3 and 5, with the machined hubs 34 on the outside of the blade assembly, and one hub 35 of each female blade inside and adjacent the hub 34 of the opposing blade. The hub 33 of the male blade- I3 is next inserted between the unfinished hubs 35, with the shoes or bosses 36 in working :5

' contact with the finished surfaces of hubs 34.

is supported against tilting movement which would otherwise occur due to the relatively short the blade or scoring of the cylinder walls is thus eliminated.

As previously explained the hollow extension or neck portion I9 projecting from cover plate 9 serves as a stufling box for preventing t5 the leakage of fluid around drive shaft I8. A preferablybronze or brass bearing 38 snugly seated within the inner end of extension I9 encircles the inner end of the shaft I8. adjacent the inner extremity thereof and abuts against 40 a collar H on the shaft. This collar precludes shaft I8 from being forced outwardly through its bearing, with possible damage to the piston blades. The outer end of extension I 9 is closed by means of a cap 5|, between which and the t5 shaft is inserted a preferably porous bearing 42. and encircling this bearing is an' oil chamber 43 formed in the cap. Oil is fed to chamber 43 through a filling opening 44. A plurality of packing rings 45, preferably of asbestos, are resiliently held against the inner end of cap 5|, by a coil spring 46 which seats at one end against the innermost packing ring and at its other end against a shoulder 48 formed in the bore 49 of extension I3. An alemite fitting 52 55 provides means for inserting grease or the like.

The salient feature of my improved stufliug box resides in the relative location of the spring 46 and packing rings 45. so that the spring and pump pressure act together upon-the packing 60 rings. Thus, when the pressure in the pump is high fluid will be forced into bore 49 through a passage 56, communicating at opposite ends with the cylinder 4 and bore 49 respectively, and the packing rings will then be compressed 65 against cap 5|, under the combined action of spring pressure and fluid pressure from the pump. conversely, when the pressure in the pump drops, the packing rings will expand against the combined pressure of the spring and the re- 70 duced pressure in the pump. It will be noted that by placing the spring between the packing rings and the pump, all danger of the packing eliminated. 76

nuances Having thus described my invention what I claim is:

l. A rotary pump comprising a working chamber, an eccentrically mounted directly driven rotor in'said working chamber, three blades embodying substantially shortened inner portions concentrically mounted within said working chamber and slidabiy engaged with said rotor and a shaft pivotally supporting said blades, said blades including a male blade having a central hub portion and lateral supporting shoes symmetrically spaced from opposite ends of said hub portion, and two female blades each having two spaced hub portions unsymmetricaliy ar ranged with respect 'to the tmnsversal axis of said blade to locate one hub portion of each blade adjacent to the hub portion of said male blade and align the other'hub portion of each female blade with one supporting shoe of said male blade.

2. A rotary Dump according to claim 1, embodying two female members of the same shape and form inverted with respect to each other to eifect their proper position with respect to the male member.

3. In a rotary pump, a working chamber provided with inlet and outlet passages, a hollow directly driven rotor member within said chamber and coextensive therewith eccentrically mounted therein and contacting with the wall thereof between said inlet and outlet passages, three blades embodying substantially shortened inner portions concentrically arranged with respect to said chamber and in driving connection hub portion of the male 3 with said rotor, and a stud shaft supporting said blades, said blades including a male blade having a central hub portion and symmetrically ar-' ranged supporting shoes at opposite sides of said hub portion, and two female blades having 5 spaced hub portionsdiiferently spaced from the transversal axis of said blades to locate one hub portion of each female blade adjacent to the hub portion of said male blade and align the other hub portion of each female blade with the respective supporting shoe of said male blade.

4. A rotary pump comprising a working chamber, an eccentrically mounted directly driven rotor in said working chamber, three blades ,embodying substantially shortened inner portions concentrically mounted within said working chamber and slidably engaged with said rotor and a shaft pivotally supporting said blades, said blades including a male blade having a central hub portion and lateral supporting shoes equally spaced from opposite ends of said hub portion, and two female blades of uniform shape and form each female blade having one finished and one unfinished hub portion differently spaced from the transveral axis of said female blade to locate the unfinished hub portion adjacent to the member and the finished hub portion opposite and in alignment with one or the other of said supporting shoes, 30 when the three blades are assembled with the female members inverted with respect to each other.

JOSEPH F. JAWOROWSKL 

